Circulating pump



Nov. 18, 1969 BALL 3,478,689

CIRCULAT ING PUMP Filed Aug. 2', 1967 '7 Sheets-Sheet 1 INVENTOR ZOWZA/Vfi 5,444

BY gf TTOZAAH Filed-Aug 1967 Nov. l8, 1969 REBALL 3,478,689

CIRCULATING PUMP 'T Sheets-Sheet :3

/ INVENTOR A/fi 56AM Nov. 18, 1969 R. E. BALL 3,478,689

CIRCULATING PUMP Filed Aug. 2, 1967 7 Sheets-Sheet 4 INVENTOR ZOWA/Vfl 5. 5 444 /ZJTW Nov. 18, 1969 R. E. BALL 3,478,689

CIRCULATING PUMP Filed Aug. 2, 1967 7 Sheets-Sheet 5 INVENTOR Kama/W0 6. 5 444 A TTOZ/Vfy Nov. 18, 1969 R. E. BALL 3,478,689

CIRCULATING PUMP Filed Aug. 2, 196 7 Sheets-Sheet 6 INVENTOR fflWA/Vfi 5- 5,444

A TTOZ/Vy United States Patent 3,478,689 CIRCULATING PUMP Rowland E. Ball, Long Beach, Calif., assignor to Borg- Warner Corporation, Chicago, 111., a corporation of Illinois Filed Aug. 2, 1967, Ser. No. 657,978 Int. Cl. F04d 13/06, 1/00; H02k 9/16 US. Cl. 103-87 8 Claims ABSTRACT OF THE DISCLOSURE The provision of a compact, unitary, combination of high pressure-high temperature hydrocarbon reactor circulating pump and an electric motor, with an improved cooling, heat repelling and heat dissipating arrangement for temperature regulation of the motor. There is also a unitary, combined thermal plate and pump diffuser removably attached to the pump cover body for facilitating assembly, service, repair, and replacement.

BACKGROUND OF THE INVENTION This invention is primarily directed to reactor circulating pump assemblies for use in the pumping of high temperature fluids under extreme pressure conditions, such, for example, as are used in the distillation of hydrocarbons.

In the past, it has been diflicult to provide a pump assembly for a high temperature-high pressure installation, including the power means which is usually anelectric motor, in a compact unitary arrangement because of the difiiculty of keeping the motor at a sufficiently low temperature to prevent damage due to the heat developed by the motor and that conducted to the motor from the fluid in the pump chamber. The practice has necessarily been to isolate the motor in a separate housing or at a considerable distance from the pump, thus making it a separate installation. It is desirous from both the standpoint of the pump manufacturer and the user, and especially from the standpoint of the former, to be in a position to warrant and service the entire installation as a unit, and to provide a compact, unitary assembly which can be shipped, installed, warranted and serviced as a unit. While this has not been too difficult where high temperatures and high pressures are not factors heretofore, to applicants knowledge, the combination of a pump and motor in such an installation has not been commercially feasible, and there exists none such that has been successful.

SUMMARY It is an object of this invention to provide a compact combination pump and motor as a unit suitable for high temperature and high pressure use.

It is another object to provide such an arrangement wherein various improved means are combined to cool and to lubricate the motor and the shaft seal.

It is another object to provide such an arrangement wherein the cooling means for the assembly does not unduly impose on the heated fluid being pumped a cooling factor which seriously reduces the high temperature necessary for the fluid being pumped.

In this connection, it is an object to provide an arrangement whereby the charging liquid for the pump contributes to, or is used as one of the cooling means employed for, the protection of the motor.

It is a further object of the invention to provide an improved lubricating and cooling arrangement for the motor and motor shaft seals; and it is a further purpose of the invention that the lubricating arrangement for the motor also serves to lubricate the seals and bearings for the motor shaft; also that a portion of the lubricant so Patented Nov. 18, 1969 pump cover body between the pump and motor wherein novel cooling means are provided, using motor lubricant, pump charging fluid, and other cooling fluid such as water, and providing a novel fluid circulation arrangement and means effectively blocking the flow of excessive heat from the pump chamber to the motor.

It is a purpose to provide an improved combination of a thermal plate andpump cover body wherein both are combined to form fluid passages for cooling liquid therebetween. In this connection, applicant proposes to disclose a novel arrangement of such fluid passages, as well as the fluid passages in the pump cover body.

It is an object in this connection to provide the pump cover body with a lamina of stainless steel on top thereof, thus preventing both corrosion of the pump cover body and excessive heat transfer between the pump and the motor.

It is a further object to provide an improved water jacket for the dissipation of heat conducted from the interior of the motor housing.

It is also a purpose to disclose a sinuous flow path means for lubricant and cooling liquid across the outer circumference of the motor stator, in which the cooling lubricant travels axially across the stator several times in its cooling circulation and in which an improved wiping action, removing heat from the motor and transferring it to the motor housing from which it is radiated to the water jacket, is obtained.

In connection with the above, it is an object to provide an improved arrangement for the lubrication and cooling of the seal and seal area by the fluid used to lubricate the motor.

Other objects, purposes, and advantages of the invention will be hereinafter described or will become apparent to those skilled in the art and the novel features of the invention will be defined in the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevational view of a pump, motor and auxiliary pump assembly, illustrating the combination of the present invention in its preferred operating position;

FIG. 2 is a longitudinal-sectional view showing the details of construction of the device of FIG. 1;

FIG. 3 is a fragmentary longitudinal-sectional enlargement showing details of the auxiliary pump illustrated in v the lower portion of FIG. 2;

FIG. 4 is a fragmentary cross-sectional view taken on the line 44 of FIG. 2, looking upward in the direction indicated by the arrows;

FIG. 5 is a fragmentary cross-sectional view taken on line 5-5 of FIG. 2, looking upward in'the direction indicated by the arrows;

FIG. 6 is a perspective view illustrating the arrangement of oil circulation channels on the stator and the spacer sleeves to provide a flow path for cooling the motor;

FIG. 7 is a development view illustrating by projecting on a plane the surface arrangement shown as cylindrical in form in perspective in FIG. 6;

FIG. 8 is a fragmentarycross-sectional view taken on the line 88 of FIG. 2, looking upward in the direction indicated by the arrows, and showing primarily details of passages and the flow pathof one arrangement used in cooling the assembly;

FIG. 9 is a fragmentary longitudinal-sectional enlargeinent of the shaft seal arrangement, pump cover body, and 'th'ermal plate shown in the upper portion of FIG. 2; v

' FIG. 1'0is a view showing'the underside of the thermal plate which is positioned between the main pump impeller and the pump cover body, and illustrating in dotted lines integral diffuser vanes; and

'- FIG. 11 'is a vertical cross-section taken on the line ll-11 of FIG. 10, looking in the direction of the arrows.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring more in detail to the construction shown in the drawings, and referring first primarily to FIGS. 1 and 2, there is here disclosed a pump and motor combination consisting of a main pump 11, an electric motor 12, and anaiixiliarypump 13, all located within a housing assembly14.

The main pump 11 is located within the pump case 15, which forms the upper portion of the housing assembly 14, and the motor 12 is housed within the motor shell 16. Between the main pump 11 and the electric motor assembly 12 there is located the pump cover body 17, which, among its other functions, forms a portion of the housing assembly 14 along with the motor shell 16 and pump case 15. The housing assembly 14 is completed by a bottom flange 20 and the motor shell cover 18, which closes the lower end of the housing assembly 14 and completes the enclosure of the motor and auxiliary pump assembly.

The pump case 15 has the depending flange 19 which is drilled and threaded to receive studs 21 spaced at intervals around its circumference.

The motor shell 16 at its upper end terminates in an outwardly extending motor shell flange 22, which is provided with holes therethrough positioned to correspond with the position of the studs 21, whereby the flange 22 receives a stud 21 through each hole. Each of the studs 21 is threaded on its depending end and receives a nut 23 by means of which the flange 22 of the motor shell 16 may be attached to the pump case 15.

It will be noted that the flange 19 is provided with an undercut or shoulder 24 enlarging the internal circumference, as is obvious from FIG. 2, and is also provided with a second shoulder extending radially inward a slight distance. The land formed on the underside of shoulder 24 provides a seat complementary to the land formed on the top of the pump cover body 17. A suitable seal means, such as spiral wound gasket 26, is inserted between the land formed by the shoulder 24 and a corresponding land on the pump cover body, whereby leakage of fluid from the pump between the pump case 15 and the pump cover body 17 is prevented. The pump cover body is also provided with a radially outwardly extending flange, as shown at 27, on which the bottom land of the flange 19 seats. Thus, when the nuts 23 are tightened, the pump cover body will be securely clamped between the flange 22 of the motor shell and the flange 19 of the pump case.

Referring to the motor shell cover 18 at the bottom of the housing assembly, it is attached to the bottom flange 20 of the motor shell 16 by means of circumferentially spaced cap screws 28 which extend through the cover 18 and are threaded into the bottom flange 20, as will be clearly apparent from FIGS. 1 and 2. a

The motor shell cover 18 has an upwardly extending flange 32 which forms a rim that fits into the undercut in the internal diameter of the bottom flange 20. A seal, such as O-rin'g seal 33, is provided to prevent leakage of fluid around thecircumference of the motor shell cover 18 at its juncture with the bottom flange 20. I

The motor shell 16, in practice, may be made up in segments which are welded together to facilitate assembly of the mechanisms therein, of which one segment com- 29 and 31.

Attached to the bottom flange 20 and extending into the inner diameter of said bottom flange is the bearing housing cover 34, which serves several functions as will be apparent hereinafter. Thisbearinghousing cover 34 is disc-shaped and has an attaching flange 35- which extends radially. outward and 'a vertically extending flange 36. The bearing housing cover 34 is spaced from the motorshell cover 18 to forma fluid area 37; and tliebear'ing housing cover 34 is attached to the bottom flange 20 by any convenient means, such as cap screws 38, located at spaced circumferential intervals around the attaching flange 35.

Referringto the pump cover body 17 in the upper part of FIG. 2, and positioned between the pump case 15 and the motor shell'flange 22 (see'also FIGS. 9, 10 and 11), there is provided a thermal plate '39. This thermal plate 39 has a depending diffuser ring 41 which, in the example shown, is separately constructed and welded to the thermal plate 39, as shown by the weld 42, to form an integral subasse-mbly. Thering 41 and the thermal plate 39se'at within the innercircumference of the pump case 15. This arrangement is clearly evident from FIGS. 2 and 9, in particular. The ring, 41 and the thermal plate 39 have their outer circumference grooved, as shown by the groove 43, at their juncture to provide an annular opening for the receipt. of threaded studs 44 whichextend into threaded holes provided therefor in the pump cover body 17. At spaced circumferential intervals, the ring'flange 41 is drilled to receive studs 44; and a nut 45 i for each stud 44 is threaded to the stud to draw the thermal plate39 and its attached diffuser ring 41 into firm engagement with the pump cover body 17, as will be apparent from FIGS. 2 and 9.

Further, as likewise will be apparent from FIGS. 2, 9 and 11, thermal plate 39 has, preferably integrally therewith, a pump diffuser 46, whereby said thermal plate 39, diffuser ring 41, and pump diffuser 46 may be re- :moved and replaced as a unit after removal of the pump case 15, by removal of the nuts 45, inserting the new or serviced unit in place, and replacing and tightening thenuts 45. In this connection, it is also sometimes necessary toservice the seal areas of a pump of this character, and ease and speed of obtaining accessthereto ,by removal of the thermal plate 39 is a real advantage and saving. Additional details of this thermal plate diffuser assembly will be explained later, especially in connectio with the pump cooling and fluid circulation.

As will be-noted, particularlyfrom FIG..9.,. the'upper surface of the pump cover body 17 has formedthereon or attached thereto by any convenient means, such as welding, electroplating, or the like, a lamina or. layer of stainless steel 40. This serves two purposes,.the principal one of which is to prevent corrosion and deterioration of the' uppersurface of the pump cover body 17 due to the corrosiye effect of fiuid In this connection, the pump cover body '17 is ordinarily constructed of carbon'fsteel, and pump fluids contacting'this surface would normally be cr-ude'oil or oil in theprocess of being refined'and having a temperature on the order of 500 F., containing corrosive impurities of both a chemical and phy-sicaljna ture. Also, the thermal plate 39 is normally made of stainless steel. The second purpose served by the staihlesssteel lamina 40 isthat of enhancing the heat barrier effect, since it is well knownthat laminations form a poor conduct rnfo r heat transfer. A. possible third benefit is the strengthening effect of theistainless steel on lthecarb'on steel pump cover body.

Asbestevident'in FIG. 9, the pump coverbody 17 is bored from the top partway down, as shown at 47,, and is thencounterbored ,on a reduced diameter, as shown at 48, thereby forming .a stepped longitudinally extending opening through the pump cover body' in the center there-. of. Extending into the bore 48 from the top is a flanged element, hereinafter termed seal housing, 49, the seal housing being held in place by one or more cap screws 50 extending through the flanged portion thereof and into the pump cover body 17, as is obvious from the drawing. A ring seal 60 is provided between the flange of the seal housing 49 and the pump cover body 17 to inhibit fluid leakage.

The seal housing 49 has a reduced outer diameter, as shown at 51, extending a substantial part of the 'distance between the ends of the seal housing to form a fluid chamber 52 between the seal housing 49 and the bore 47.

At its bottom end, the seal housing 49 has an outer diameter extending to the bore 47, but is provided with a series of fluid passages, such as serrations, notches or flats 53, whereby fluid in the fluid chamber 52 is in communication with the bore 47 below the end of the seal housing 49.

Near its upper end, the internal diameter of the seal housing 49 is grooved or undercut, as shown at 54. A hole 55 is drilledfrom the chamber 52 into the undercut 54, whereby fluid communication is established between said chamber and said undercut. The seal housing 49 has formed on its internal diameter intermediate the ends a ring flange 56 which serves as a stop for axial movement of the fixed or nonrotating seal face 57 in an upward direction.

A grooved sleeve 58 is inserted into the seal housing 49 and is attached thereto in fluid tight relation near its top in any convenient manner, such as by welding. The grooved sleeve 58 is undercut radially inwardly on its outer diameter, as shown at 59, which undercut is complementary to and mates with the undercut 54 in the seal housing to form an annular chamber 61. At its lower end, the sleeve 58 is provided with a reduced diameterto provide an annular chamber 62 between the outer circumference of the end portion of said sleeve and the inner circumference of the seal housing 49; and, as indicated at 63, a hole or opening is provided, which may be in the form of a radial slot cross the bottom land of said sleeve 58, placing the chamber 62 in fluid communication with the interior of the sleeve 58. The outer circumference of the sleeve 58 has a spiral groove 64 which extends from the chamber 62 to the chamber 61 and serves as a pressure reducing cell. In this way, fluid under pressure in the chamber 61 is caused to leak at reduced pressure into the chamber 62 and through th eslot 63, all aswill be described later. Referring to the counterbore 48, there is provided a radial sleeve bearing 65 into which extends a drive shaft 66. The bearing 65 serves to support such shaft 66 at the pump end of the assembly. This shaft 66, above the hearing 65, is reduced in diameter to provide a 'stop 67 for a rotary sleeve 68 which surrounds the shaft 66 and is attached thereto by any convenient means, such as by threading thereto as shown at 69. Also, the sleeve is provided with a set, screw 71 which holds the sleeve 68 against rotation with respect to the shaft 66. Mounted on the sleeve 68 is rotary seal face 72, spring retainer 73, and springs 74, all attached to the rotary sleeve 68 and thus drivingly attached to the shaft 66 by means of the set screw 75, sleeve 68, and set screw 71.

g The details of the seal assembly, except to the extent necessary to show the features-of operation of the present disclosure are not described herein, as the seal forms the subject matterv of a separate application for United .States patent by FernandoG. Marrujo and Winfred I.

' owned.

It will be well 'to mention that the drive shaft 66 extends from the interior of the pump case 15 longitudinally through the entire housing assembly 14, terminating within the bearing housing cover 34. Further details with respect to the assembly and lower bearing support for the drive shaft 66 will be described later.

At its upper end, as will be apparent from FIGS. 2 and 9, the drive shaft 66 extends through a central shaft opening 76 in the thermal plate 39 and has mounted thereon the impeller 77 of the main pump 11, said impeller being retained in place by the threaded collar 78 which is threaded onto the end of the shaft 66, and a cap screw 79 threaded into the end of the shaft 66 and passing through the collar 78. A key 81, positioned in a key slot on the shaft 66 and a matching key slot in the hub of the impeller 77, drivingly connects the impeller 77 to the shaft 66.

The drive shaft 66, at its upper end, is drilled or formed with a longitudinally extending bore 82 terminating below the top. In actual practice, this drive shaft may be formed in sections and welded as shown at 83. The bore 82 has an enlarged diameter in the area extending from just above the weld 83 downward to a point 84, into which is inserted a flanged sleeve 85.

The drive shaft 66 has a hole 86 drilled axially from the outer circumference of shaft 66 into the bore 82 to form a passage for fluid from the bore 47 in the pump cover body 17 into the bore 82 in the shaft 66. The flanged sleeve 85 extends upwardly to the vicinity of the top of the bore 82, and fluid entering through the hole 86 from the bore 47 to the bore 82 is deflected upwardly around the upper end of the flanged sleeve 85 and flows downward through the interior of the sleeve 85, again entering the bore 82 below the bottom of the flanged sleeve 85.

The drive shaft bore 82 is continued downward for a distance which reaches a position below the bottom of said pump cover body 17; and, at a position adjacent its bottom, said bore 82 is provided with passages 87 which, in the embodiment shown here, consist of a hole drilled axially through the shaft 66 providing two passages leading from the bore 82, whereby fluid in said bore 82 may escape into the motor shell 16.

The shaft 66 is enlarged as shown at 88, and mounted thereon is the rotor 89 which is formed on and drivingly connected with the shaft 66. Beneath the enlargement 88 theshaft 66 is reduced in diameter as shown at 98 and is mounted in a sleeve bearing 91, as is clearly apparent in FIG. 2. The sleeve bearing ,91, in turn, is fitted within the inner diameter of a bearing housing sleeve 92 which has an annular flange 93 near its bottom perforated at spaced intervals around its circumference to receive the cap screws 94, whereby said bearing housing sleeve 92 is attached to an inwardly extending annular flange 95 on the bottom flange 20 which forms an integral part of the housing assembly 14. Thus, the sleeve bearing 91 for the shaft is supported through the bearing housing sleeve 92 and housing assembly 14. This firmly holds the shaft 66 in place at its lower end. The shaft 66 is further reduced in diameter, as shown at 99, and extends through the auxiliary pump 13. At its bottom end, the drive shaft 66 is provided with a thrust disc nut 96 which is threaded onto] said drive shaft and which is held against rotation with respect to said shaft 66 by the set screw 97.

Referring again to the pump cover body 17, and referring to FIGS. 2, 8 and 9, extending at an angle from a fluid chamber 101 formed by a counterbore in the top internal diameter of the motor shell 16, the bottom surface of the pump cover body 17 and an upper stator spacer sleeve 102, are the fluid passages 103 extending to the pump cover body bore fluid chamber 52. In actual practice, four of the fluid passages 103 connect the chamber 101 to the chamber 52. It may be noted that oil for cooling and lubrication flows upwardly through said passages 103 for lubricating the seal and for other purposes. This will be clarified later in the description.

Also, as will be clear from FIG. 8, what may be referred to as a pump cover body water conduit circuit is provided, comprising a series of holes 104 drilled at circumferentially spaced intervals from the circumference generally toward the center of the pump cover body, preferably at an upward angle. Each of these holes intersects another of the holes as shown at 105 (FIG. 8), the arrangement being such that the holes may be said to be in pairs, so that each pair of holes connects into the contiguous pair at their inner ends. Also, except for the inlet and discharge holes, each pair of holes is connected by a fluid passage 106 at its radially outer ends. One hole of the series is tapped to receive a fluid conduit (not shown) and forms an inlet 107 whereby fluid, usually cold water, is introduced into the circuit; and another hole is tapped to receive a drain connection and forms an outlet 108 for discharge of fluid from the circuit. Thus, fluid, such as cold water, is introduced through the inlet 107, travels to what may be termed the radially inner end of the inlet hole 107 to the intersection 105, and then back radially outward through the first connecting hole 104, through the fluid passage 106, into the next circumferentially spaced hole 104 and so on, through the entire circumferential arrangement to the discharge 108. By this means, cooling water is enabled to travel through the pump case body in what may be termed a zigzag manner and in such a way as to exert maximum cooling effect and efliciently dissipate substantially all of the heat from the pump cover body before it can reach the motor. This is extremely important since the temperature in the main pump may be on the order of 850 R, which temperature must be reduced before it reaches the electric motor so that the latter will be maintained at, for example, 110 F. to 150 F., to prevent damage to the motor windings, which must ordinarily not exceed 150 C.

Referring next primarily to FIGS. 10 and 11, and reference still being had to FIGS. 2 and 9, the construction of the thermal plate 39 with its integral diifuser 46 is considered unique and important, both from a service standpoint and as an improved heat barrier, in the construction of a pump motor combination, such as that disclosed herein, whereby the motor assembly 12 may be located in the same housing assembly 14 and in close relationship to the pump assembly 11 for the pumping of extremely hot, corosive fluids, while aiding in maintaining the temperature of the motor 12 within safe limits to prevent damage thereto. This thermal plate 39 has, as mentioned previously, the integral pump difiuser 46 which is preferably formed integrally therewith. The diffuser 46 in the arrangement indicated has a series of vertical curved vanes 109 spaced around the circumference and an annular integral ring 111, which ring surrounds the inlet port 115 for the main pump 11. The ditfuser vanes 109 form the fluid flow path of liquid discharged from the main pump impeller 77. As is apparent from FIG. 2, a wear ring 112 fits over the annular ring 111 and is attached thereto by a series of cap screws 113. The wear ring 112 extends downward into the internal circumference of the annular ring 111 and receives an inlet conduit 115 by means of which the fluid to be pumped reaches the main impeller 77 The impeller blades 114 of the main impeller are joined to an impeller ring 120 at their upper edges, in the well known manner.

On its underside, the thermal plate 39 is provided with a series of what may be termed partially annular concentric grooves, 116, 117, 118 and 119, formed by the outer depending rim flange 121, and the depending spaced ridges 122, 123, 124 and 125, which ridges are concentric with the rim flange 121 but extend circumferentially to a short distance less than a full 360". At the end of each ridges (except the innermost, 125) a barrier or fluid diverter is' provided extending radially inwardly across the adjacent, radially inward groove. In the arrangement of FIG. 10, the groove 116 hasthe barrier 126 which extends radially inwardly from the rim flange 121 to the ridge 122; the groove 117 has the barrier 127 which extends from the ridge 122 to the ridge 123; the groove 118 has the barrier 128 which extends firom the ridge 123 to the ridge 124; and the groove 119 has the barrier 129 which extends from the ridge 124 to the ridge 125.

When the diffuser ring 41 is attached, as pointed'out earlier, to the thermal plate 39, it forms a bottom closure for groove 11-6 and thus completes a fluid passage; and when the pump cover body 17 is attached, it forms a bottom closure for the remaining grooves 117, 118 and 119, to make them into fluid passages. Since the ridges 122, 123, 124, terminate short of a full circle, each passage 116, 117, 118 thus opens into the next radially inward passage 117, 118, 119, so that a flow path for fluid,

' spiral-like in arrangement, is created. Although the above indicated grooves 116, 117, 118, 119 are more easily manufactured, and are believed to be more eflicient, actually a series of spiral grooves or possibly other shapes would serve the purpose. The series of passages including grooves 116, 117, 118 and 119, the hereinafter described inlet 131, concentric channel 133, fluid chamber 135, and annular space 136, may be herein collectively referred to as the thermal plate cooling system. The passage described as groove 116 has a fluid inlet provided by the right-angle inlet bore 131 through the difluser ring 41. This bore 131 is preferably connected to the source of fluid used to charge the main pump 11. As contemplated here, this Will comprise crude oil, possibly at as much as 500 F. temperature.

The underside of the thermal plate 39 has an enlarged, upwardly extending bore 132 concentric with the shaft opening 76 and extending upwardly a distance somewhat above the upper extent of the grooves 116-119, and the top of the bore 132 has an upwardly extending concentric channel 133. The radially inner side of the channel 133 comprises the outer periphery of the depending ring flange 134 which extends in width from the channel 133 to the shaft opening 76.

As will be obvious from FIGS. 2 and 9, particularly the latter, when the thermal plate 39 is in place, the heads of cap screws 50, which fasten the flange of the seal housing 49 to the pump cover body 17, extend into the channel 133. Further, the flange of the seal housing 49 is spaced a short distance from the bottom of the bore 132 and also is located radially inward from the side of said bore 132, whereby the fluid chamber 135 is created which leads through the channel 133, across the top of the flange of the seal housing 49, across the top of the grooved sleeve 58, and discharges into the annular space 136 between the sleeve 68 and the grooved sleeve 58'. At the intersection of said fluid chamber 135 with the annular space 136, fluid is caused to flow through the shaft opening 76 where it is discharged between the im peller 77 and the thermal plate 39. It will be picked up by vanes 137 on the bottom of the impeller 77 and mixed into the fluid in the main pump 11 from where it is discharged into the diffuser 46. It should be noted that fluid from the groove 119 enters the fluid chamber 135, past the end of the ridge 125 which terminates short of the barrier 129, as above described. Thus, fluid entering the inlet bore 131 is picked up by the groove 11-6, proceeds into grooves 117, 118 and 119, is discharged into the fluid chamber 35, flows through the channel 133, across the top of the flange of the seal housing 49 and grooved sleeve 58 beneath the bottom of the ringflange 134,-into the annular space 136, upwardly around the shaft 66 through the'shaft opening 76, and outwardly beneaththe impeller 77 where it is picked up and discharged by the vanes 137 on the bottom of 'said impeller. At the -clischarge of the fluid from the chamber 135 into the annular space 136, fluid from said annular space is mixed' with a relatively small amount of seal lubricating fluid from charged beneath the impeller 77. Since the fluid entering the motor lubrication system, and the mixture is disthe inlet 131 is usually fluid taken from the source for the main pump inlet 16, it may have physical (such as fines from a catalyst) and chemical impurities. It is desirable that there be a flushing action created which includes some motor oil to. keep the lubricant passages clear and prevent the building up of harmful deposits beneath the main impeller 77 which could cause blockage and/ or consequent wear to that impeller and the thermal plate 39. The temperature of the fluid entering-through inlet 131 may, as mentioned above, be on the order of 500 F., and, in the example shown herein, it is contemplated that the flow would be possibly 25 gallons per minute. Such fluid flowing through the grooves 116, 117, 118, 119, as above-mentioned, will thus normally be several hundred degrees lower in temperature than the fluid in the main pump chamber 15and thus will cause a considerable cooling before the heat from the main pump chamber reaches the pump cover body 17.

Referring next to the auxiliary pump construction and various lubricating passages, and referring particularly to FIGS. 3 and 4, with occasional reference to FIG. 2, the drive shaft 66 has attached thereto at the reduced shaft diameter 99 a thrust disc 138 which, in the example shown here, is attached to the shaft by means of the key 139. Thus, the thrust disc 138 rotates with the shaft 66.

On each side of the thrust disc 138 is located a thrust bearing shoe, here shown as the upper and lower thrust bearing shoes 141 and 142, respectively. These shoes are preferably segmental in form and loosely inserted so that they may tilt for proper alignment and to compensate for distortion, etc. These shoes are free to float, but do not rotate with the shaft 66. As shown in connection with shoe 141, each shoe has a button 143, which is also true (but not shown) for the shoe 142. These buttons 143 are loosely fastened to their respective shoes 141 and 142 by any convenient means (not shown), and the button for each shoe engages a corresponding leveling plate, of which the leveling plate 144 is shown. These leveling plates are positioned in an annular ring 145 and held loosely therein by means of a screw 146 which extends through the ring 145 and into an aperture provided on the outer surface of the leveling plate. A similar arrangement applies, although not shown, to annular ring 147. This construction will be clear from FIG. 3. r

The leveling plates 144 are alternated in the annular rings 145 and 147 with rocker plates 148, one of which is shown in the ring 147, which rocker plates 148 are each loosely attached to the respective rings 147 and 145 by means of dowel pins 149. By this means, the parts comprise a rather loose, self-adjustable assembly in which the shoes 141 and 142 are free to tilt, and wherein the lubricating fluid between the thrust disc 138 and the shoes 141 and 142 builds up, by what may be termed a Wedging action, a lubricating and self-adjusting support between said parts which is relatively free of friction. It is noted that because of the segmental construction of the shoes 141, 142 and associated parts, oil for lubrication and cooling can flow therearound with facility.

The thrust disc 138, upper and lower thnlst bearing shoes 141 and 142, buttons 143, leveling plates 144 plates 148, and rings 145 and 147 comprise a form of Kingsbury-type thrust bearing (see United States Letters Patent No. 1,378,544, issued May 17, 1921), which is well known and has been commercially available. The description herein is primarily in order that the fluid flow forming a feature of this invention may be clearly evident when hereafter described.

Mounted on the thrust disc 138 is a ring-type impeller 151. This impeller is drivingly attached to the thrust disc 138 by means of a Woodruif key 152. A pump ring 153 is attached to the bearing housing sleeve 92 by any convenient means (not shown), and the pump ring 154 is attached to the bearing housing cover 34 by means of one or more screws 155. These pu-mp rings form the side walls of the impeller chamber and, as Will be apparent from FIGS. 3 and 4, are each undercut as shown at 156 and 157 to form with a mating groove 158 in the bottom flange 20 an inlet chamber 159 for fluid to be pumped. It is noted that the thrust disc 138 is grooved circumferentially on either side of the impeller 151, and retainer rings 161 and 162 hold the impeller against sidewise movement of a suflicient amount to cause it to bind on either pump ring 153 or 154.

The pump is provided with a discharge chamber 163, shown partly in dotted lines in FIG. 3 and in full lines in FIG. 4. From the chamber 163, on each side of the impeller 151, there is provided a fluid passage in the form of a hole 164 drilled through the pump ring 153 and a hole 165 drilled through the pump ring 154 between the discharge chamber 163 and the annular fluid chambers 166 and 167, respectively. By this means, fluid from the pump discharge chamber 163 enters the annular chambers 166 and 167. The principal portion of the discharged fluid from the pump passes outward from 163 and enters a conduit 168 formed by drilling downwardly from the upper surface of the bottom flange 20 to intersect said discharge chamber 163.

The bottom flange 20 also has a port 169 drilled from its upper surface through the flange and intersecting the inlet chamber 159. The bearing housing cover 34 has a mating hole 171 drilled in its outer flange and positioned to mate with the port 169 of the bottom flange, whereby fluid from the fluid area 37 may flow into the pump inlet 159 and also fluid from the motor chamber at the top of the bottom flange 20 may flow into said pump inlet The motor shell cover 18 has a fluid opening 172 therethrough leading into the fluid area 37, whereby a supply of lubricant fluid may be constantly furnished to the interior of the housing assembly 14.

As will be apparent from FIG. 2, the fluid opening 172 in the motor shell cover 18 connects to a source of lubricating oil for replacing fluid lost from the circuit so there is a constant supply for lubricating and cooling the motor assembly, seal, etc.; and a check valve 173 (indicated only diagrammatically) is preferably provided to control the flow of such oil into the housing assembly 14 and to prevent its flow from the fluid area 37 in a reverse direction.

The bearing housing cover 34 has its bottom perforated by means of a drilled hole or the like 174, thus placing the interior of the bearing housing cover in fluid communication with the fluid area 37.

It will be noted from FIG. 3 particularlyfthat the conduit 168 from the discharge of the auxiliary pump impeller 151 is in fluid communication with the exterior o; the lower spacer sleeve 175, as will be described herea ter.

Referring to FIGS. 5, 6 and 7, the construction of the stator 176, the upper stator spacer sleeve 102 and the lower stator spacer sleeve 175 are illustrated more in detail, reference also being had to FIG. 2 to illustrate their installation in the motor assembly. As shown in the latter figure, the stator 176 has end windings 177 and 178, the windings 177 being located at the lower end of the stator and the windings 178 being located at the upper end of the stator.

The stator 176 is composed of a series of laminations in the usual manner which are notched about their peripheries with aligned notches to provide stator ridges 179 extending transversely across the stator assembly and the stator grooves 181 between the stator ridges 179. As is clearly apparent from FIG. 6, there is thereby created a series of alternate channels and ridges; and when the stator is press-fitted into the motor shell 16 there is thus formed a series of passages or fluid flow paths axially on the outer circumference of the stator. As mentioned, the stator 176 is, in production, ordinarily press-fitted or shrink-fitted into the motor shell 16 so that the outer lands of the stator ridges 179 engage the motor shell 16 and hold the stator firmly in place and properly aligned and provide such fluid flow paths whereby heat from the motor'will be dissipated by fluid in said axial flow path across the stator which, in turn, conducts heat through the motor shell 16.

"The electrical conduit 182 for the electrical terminal connections (not shown) to the end windings 177 contains the wiring to the terminal studs or lead-in connections 183, 184 and 185 (see FIG. collected for protection thereof and these, in turn, as shown in FIG. 2, lead to the junction box 186. Since the electrical connections are unimportant for'this disclosure, no further reference need be made thereto. It may b state that, as contemplated, the electric motor 12 is a three-phase 440 volt motor.

Referring again to FIGS. 2, 3, 5, 6 and 7, the sleeve 175 has, on the radially outer surface thereof, a raised base land 187 which extends, in the example shown, four fifths of the circumference at the base, leaving one-fifth of" its outer surface without the base land. One end of said base land 187 is provided with an upwardly extending raised'land or ridge 188, and the other end is provided with a similar ridge 189. Intermediate the ridge 188 and the ridge 189 is another upwardly extending ridge 191, In each instance, these ridges 188, 189 and 191 extend from the base land 187 to the top of the spacer sleeve. Further, each of these ridges is preferably the same circumferential width as the stator ridges 179 of the stator 176 and are positioned, when the spacer sleeve 175 is in place, to mate with a stator ridge 179 as shown at 192.

The spacer sleeve 17 5 (see FIG. 3) at its bottom has an inwardly extending flange portion 193 which, in turn, has an annular depending ring flange 194. The spacer sleeve 175 is, as was the case with the stator 176 shrink-fitted into the motor shell 16 with the base land 187 and ridges 188, 189 and 191 engaging the inner circumference of the motor shell 16. The spacer sleeve 175 is attached to the bottom flange 20 by any convenient means, such "as by the weld 195. The upper stator spacer sleeve 102 is similarly constructed insofar as its outer circumference is concerned to the spacer sleeve 175, with the top land 196 extending four-fifths of the circumference and forming a rim around the top for said four-fiifths of the distance. The raised ridges 197, 198 and 199 extend from the top land 1%, the ridge 197 extending downwardly from one end of said land and the ridge 198 from the other end of said land.

As is evident, the top land 196 does not extend between the ridges 1 97 and 198, whereas, as mentioned above, the base land 187 does not extend between the ridges 188 and 189. Accordingly, fluid entering the space, herein designated as space 201, between the lower spacer sleeve 175 and the motor shell 16, between the ridges 188 and 189, is conducted through the passages, here designated 202 (that is, over the stator grooves 181, between the statorridges 179), and into the conduit space 203 which extends from the raised ridge 198 to the raised ridge 199 acrossthe top of the stator. Such fluid willthen be directed in a. reverse path through similar stator passages 204 into the bottom conduit space 205 which extends from the ridge 188 to the ridge 191 across the bottom edge of the stator. From there the fluid will again reverse its path and flow through the stator passages 206 into the second top conduit space 207 which extends from the raised ridge 199 to the ridge 197. From the second top conduit space 207 the fluid will flow through the stator passages 208 into the second bottom conduit space 209 which extends from the raised ridge 191 to the raised ridge 189. From the second bottom conduit space 209 the fluid will flow through the stator passages 211 into the discharge space 212 which extends between the raised ridges 197 and 198. Theseries of stator passages 202, 204, 206, 208 and 211 in the example shown consists of ten passages for each series although, of course, the number 12 may be varied. It is obvious that fluid entering the space 201 will thus travel in zigzag fashion in what may be called a sinuous flow pattern in completing its trip around the complete circumference of the stator, traveling axially across the stator in the example shown five times, thereby efficiently performing its cooling function. The stator 176-andtop and bottom sleeve 102, 175 in assembly may thus be referred to as comprising'a sinuous stator cooling fluid flow path.

As will be clear from FIGS. 2 and 3, the entrance space 201is open to fluid from the auxiliary pump flowing from the conduit 168. In the example shown, this fluid is maintained at a pressure exceeding that existing at the main pump impeller 77, preferably the differential being about 250 p.s.i, Thus, the pressure in the motor cavities 214 and 216 may be approximately 2,750 p.s.i., while that in the main impeller suction area would be about 2,500 p.s.i.

At its upper end (see FIGS. 2 and 9), the discharge space 212 opens into the fluid chamber 101 which, in turn, supplies fluid to the fluid passages 103 from where it enters the fluid chamber 52, a portion serving to lubricate the seal faces 57, 72 and a second portion passing through the hole 55 into annular chamber 61 and through the pressure and flow reducing spiral groove 64 and slot 63 into annular space 136 where it mixes with the leakage across the seal faces 57 and 72, then is mixed with fluid from the passage and is discharged through the shaft opening 76 beneath the main impeller 77, picked up by the vanes 137 on the bottom thereof, mixed with the main pump discharge and leaves the assembly by way of the pump outlet 213. In the example shown, perhaps two gallons per minute of lubricating fluid is mixed with the fluid from passage 135.

The remainder of the fluid from the fluid chamber 52 passes over the seal and through the hole 86 into the bore 82 in the drive shaft 66, passes through the flanged sleeve 85 and out the passages 87 into the upper motor cavity 214, through the clearance space 215 between the rotor and the stator and into the lower motor cavity 216 below the motor. From the lower motor cavity 216 where it performs the function of lubricating the sleeve bearing 91, the fluid enters the port 169 (see FIG. 3) and returns to the inlet chamber 159 of the auxiliary pump 13 to be recycle.

It is also noted that the auxiliary pump 13 creates a pair of ancillary fluid circuits to supply lubrication and fluid primarily to the Kingsbury-type bearing assembly. As described heretofore, the pump rings 153 and 154 have outlet ports 164 and 165, respectively. The port 164 conducts fluid from the discharge chamber 163 into the fluid chamber 166 from where the fluid flows around'the elements of the Kingsbury-type bearing assembly and between the upper thrust bearing shoe 141, and the thrust disc 138, into the space formed by the clearance between the upper thrust bearing shoe 141 and the drive shaft 66, along the internal diameter of the bearing housing sleeve 92 and out the port 217 into the lower motor cavity 216, from where it flows through the port 169 into the inlet chamber 159 to the auxiliary impeller 151. Likewise, fluid from the discharge chamber 163 flows through.t he hole 165 in the pump ring 154 into the fluid chamber 167 and from there through the Kingsbury-type bearing elements and also across the bottom face of the trust disc 138, into the annular space 218 below the drive shaft 66 and inside of the bearing housing cover 34. From the annular space 218 the fluid flows through the hole 174 from where it enters the fluidarea 37. In the fluid area 37 it comingles with freshly supplied fluid through the fluid opening 172, enters the mating hole 171,-passes through the port 169 into the inlet chamber 159 of the auxiliary pump where it is again picked up by the impeller 151. V

Thus these two circuits, which may be described as the ancillary lubricating circuits, constantly supply fluid to the Kingsbury-type bearing elements and other auxiliary 13 pumpparts. It is noted that the sleeve bearing 91 also receive lubrication from the first-mentioned ancillary fluid circuit, as well as from the fluid present in the lower motor cavity 216. Y

- -'In connection with the initial supply of lubricating fluid to theauxiliary pump 13 and thus to the fluid circuits for the motor 12- and seal as above described, there is preferably provided an air-bleed 221 which, as is indicated in dotted lines in FIGS. 2, Sand 9, extends into the fluid chamber 52 whereby the system may be initially filled without entrapped air. being a problem. Of course, any relatively small amount of air will work its way through the groove 64 and out through the shaft opening 76.

- 'For the purpose of removing fluid from the main pump 11 when it is desired to disassemble'the system, or for other reasons, there is provided a drain 222. This drain is shown only in FIG. 1, as it is not important for the disclosure herein.

- To assist in removing heat from the motor area and maintaining the desired temperature, an improved heat exchange-arrangement is provided. As evident from FIG. 2, this comprises a heat exchange shell 223 surrounding the exterior of the motor shell 16 and spaced therefrom, and. attached at its upper end by any suitable means, such as welding, to the bottom of the motor shell flange 22. At its bottom end,'the shell is attached to a weld ring 224 which is welded or otherwise attached to the motor shell 16. The heat' exchange shell 223 is spaced from the motor shell .16, and there is located in said space a spiral tube 225'. At its bottom end, the spiral tube 225 is opened to the interior of the water jacket thus formed, and at its top endis similarly opened. Thus, both the entrance and exit of the spiral tube are within the water jacket, and any'fluid flowing through said tube is derived from fluid entering the water jacket. It is noted that the convolutions of the spiral tube 225 are preferably spaced so that water may flow upward in the areas between said tube convolutions; whereby such water or other fluid travels in a spiral path around and around the motor shell 16.

- -.-At its upper end, the water exits through a discharge port 226 formed by drilling a substantially vertical hole in said flange 22 for a short distance above said water jacket and drilling a radial hole intersecting said vertical hole. The water jacket has an inlet 227 whereby water under pressure canbe introduced into the interior. It is noted that this water jacket is of an unusual nature in that two flow paths, one through the tube and one around the convolutions of the tube, are created, both of which havea common inlet 227 and a common discharge 226. This assists in obtaining a more thorough contact and movement of the water with respect-tothe motor shel11-6, whereby heatis more effectively removed from the motor area. The water jacket is ordinarily attached to a source of water under pressure, such as a city water main, and cold water is thus passed through the water-jackethand over the motor shell 16. Since thefluid .flow of the lubricating and cooling fluid in the motor 12 is initially channeled against the, shell 16 by reason of the sinuous stator cooling fluid flow path as above described, said lubricating and .cooling fluid .is constantlycooled by the water jacket fluid circulation.

OPERATION [5T0 recapitulate the more important aspects of theassembly, especially with respect to theimprovedmeans for servicing :certain'critical parts, and-also toemphasize the cooling and heat control .features, it is'noted that the pump case. 15 is essentially a pressure vessel and that the reactor vessel to which the pump is connectedmay, byproper design, have provision I for receivingthe "main. impeller 77, and diffuser 46, with provision for attaching by-means .of studs. similar to the studs 21, or otherwise, the remainder of: the assembly. However, for the purposes of this description, it is assumed that, the arrangement in such .event w l he heq iva t otthe Pump .q se. :1

' Although the assembly hereindescribed may be filled with lubricating fluid before the pump cover body 17 it placed in position, provision has been made for a supply of lubricant under pressure through the check valve 173, in which event the filling would be expedited by bleeding off the excess air through the air-bleed 221. Any remaining entrapped air above the radially inner end of the airbleed 221 would normally find its way out of the assembly through the shaft opening 76.

The inlet bore 131 is preferably attached to the source (not shown) of charging liquid to be pumped. Due to the desirability in this type of pump that the liquid entering the inlet bore 131 be relatively hot, such liquid can be obtained by providing a bypass from the source of liquid used in charging the main pump 11.'It is believed that a disclosure of such bypass is unnecessary here for the reason that it is a relatively simple matter to provide such a bypass, it being understood that such a liquid is from the charging source for the main pump 11 and after it is mixed with fluids from the seals and pressure reducing spiralf64 in the 'space 136, will be at a pressure slightly above thatin the main pump chamber beneath the impeller 77 'when discharged through the shaft opening 76. The pressure at 76 beneath the impeller 77 will be less than that existing in the main pump chamber for the reason that the bottom vanes 137 exhaust the fluid from the area of the shaft opening 76. In the normal course and for the type of use disclosed herein, fluid entering the inlet bore 131 would be at a fairly high temperature, for example 500 F., and at a pressure about that of the main pump suction pressurethat is, for example, 2,500 pounds per square inch.

Since the temperature normally existing in the main pump 11 is somewhat higher than the temperature of the fluid entering the inlet bore 131the former being perhaps 750 F., and the latter 500 F.the fluid flowing through the inlet bore 131 and from there through the passages 116, 117, 118 and 119 will have a tempering effect on any heat conducted into the thermal plate 39. On the other hand, such fluid escapes through the shaft opening 76 into the main pump chamber underneath the impeller 77 after having previously been mixed with the comparatively small amount of lubricant leaking through the seal, that is, across the faces of the fixed seal face 57 and rotary seal face 72. Such fluid, because it is fairly high in temperature even after the mixing occurs, does not unduly lower the temperature in the pump chamber, a condition which would be intolerable. This flow of fluid through the shaft opening 76 may be on the order of, for example, 25 gallons per minute and is sufficient to flush out any impurities, such as fines, which would otherwise tend to pile up under the main impeller 77 and block the flow of the fluid from the passages 116, etc., and also, perhaps more important, interfere with the flow of lubricant across the seal faces, with consequent damage to the seals. The fluid escaping through the shaft opening 76 is picked up by the impeller blades 137 and carried into the'liquid being pumped by the main pump 11. It is noted that this just above-described fluid' flow does materially reduce heat escaping by conduction through the thermal plate 39, and the shape of the flow path due to the novel arrangement of the passages 116, 117, 118, 119, and 133 does cause a very effective surface contactwith the thermal plate 39, whereby the areas below the thermal plate receivevery little conducted heat from the pump chamber.

-. Effectively. assisting the retardation of heat conduction is the stainless steel lamina 40 which forms thebottom of the channels or grooves 117, 118 and 119, and which extends across the top of the pump cover body-17. Such stainless steel has the property of deflecting heat, prevents corrosion of the top of the pump cover body 17, and adds an insulating means due to its laminated characteristic. Thus it is noted that relatively hot fluid-enters the inlet bore 131,travels through the channels 116, 1 17, 118 and 119, and into the fluid chamber 135 and concentric chan nels 133, in what may be termed a generally spiral path, into the annular space 136, there mixes with any lubricant present due to leakage across the seal faces of lubricating fluid, and is discharged into the main pump chamber through the shaft opening 76. This circulation forms what may be referred to as the circulation for the thermal plate cooling system.

The pump cover body 17, in turn, has provision for both circulation of a cooling fluid such as cold water in a zigzag course, radially and circumferentially, and also provision for the passage of the motor lubricant from the motor lubricant circulating system to the seal areas, from where it is returned through the motor drive shaft 66 back to the motor housing. Such zigzag cooling passages and motor lubricant passages may be collectively referred to as the pump cover body fluid means, it being understood that the latter mentioned motor lubricant passages form a portion also of the motor cooling and seal lubricating system.

With respect to what may be referred to as the pump cover body water circulating means, as described above, the inlet 107 is connected to a cold water source, such as a city water system. Of course, an independent source of any cooling fluid would serve the purpose, but for this description the reference will be to a cold water source. The inlet 107, as described above, extends in a generally radial direction inward to where it intersects the hole 104 at the intersection 105, and the water then flows radially outward into the fluid passage 106 and then in a generally radially inwardly direction through the adjacent hole 104, and continues similarly in a zigzag fashion around and through the pump cover body 17 to the fluid outlet 108 where it is discharged in any convenient manner. It is contemplated that this zigzag water flow arrangement will remove most of the heat entering the pump cover body 17 and will reduce the temperature to below that which would be harmful to the motor 12.

The fluid passages 103 for the lubricating oil from the motor lubricating system to the seals will be tempered by the pump cover body 17 temperature, removing any heat above that of the lubricating oil or, if the lubricating oil is warmer than the pump cover body 17 at the position of the fluid passages 103, will release the excess heat into the pump cover body where at least a portion of it is removed by the water circulation system above described.

The motor and seal lubrication system has previously been described in connection with separate portions of the assembly. It is noted that lubricating fluid is introduced into the system through check valve 173 and fluid opening 172 under pressure greater than the suction pressure of the main pump 11, for example, 250 p.s.i. over the suction pressure of the main pump, and this check valve prevents any reverse flow of the lubricating fluid. From the fluid opening 172 the lubricant flows into the fluid area 37, through the mating hole 171 into the inlet chamber 159 of the auxiliary pump assembly 13. Here it is picked up by the impeller 151 and carried into the discharge chamber 163 where it is split into three circuits, two of them 164, 165 for lubricating the Kingsbury-type bearing assembly and shaft bearing (from where the fluid finds its way back into the auxiliary pump inlet 159), but the main discharge going to the conduit 168. Here the fluid enters the space 201 of the lower spacer sleeve 175 and accelerates through the passages 202 (because of restrictions) of the stator 176 where it picks up any motor heat and conducts heat to the motor shell 16 which is cooled by the water jacket.

From the passages 202 the lubricant enters the conduit space 203 where it is diverted into the passages 204, making a second pass axiliallyacross the stator 176. From the passages 204 the lubricant is discharged into the bottom conduit space 205 where it is again diverted axially across the stator through the passages 206. The lubricant is discharged from the passages 206 into the second top con-' duit space 207 and is again diverted axially across the stator through the passages 208 and into the second bottom conduit space 209. From the space 209 the lubricant passes through the stator passages 211 into the discharge space 212, having made five axial passes across the stator, picking up motor heat and conducting at least some of said heat through the motor shell 16. l

The discharge space 212 discharges into the annular fluid chamber 101 from where the fluid is conducted by the fluid passages 103 (in the example given here, four in number) into the fluid chamber 52 of the pump cover body 17. From the fluid chamber 52 a restricted amount of the lubricant flows through the hole 55 into the annular chamber 61, through the spiral groove 64 into a second annular chamber 62. From there it goes through the slot 63 into the annular space 136 where it mixes with fluid from the above-described thermal plate cooling system from the fluid chamber 135 and is discharged beneath the main pump impeller 77 through the shaft opening 76. The remainder of the fluid flows over the seals, a minute portion going across the seal faces for lubricating and cooling them, but the main portion being discharged through the hole 86 into the shaft bore 82 from where it flows through the flanged sleeve 85 into passages 87 which, in turn, conduct the fluid into the upper motor cavity 214.

From the upper motor cavity 214 the fluid passes between the stator 176 and the rotor 89 in the clearance space 215 and into the lower motor cavity 216. From the lower motor cavity 216 the fluid is returned to the auxiliary pump 13 through the inlet chamber 159 from where it starts its circuit again.

It will thus be seen that the motor lubrication system, which is also the seal lubrication system, very efliciently cools and lubricates the motor area and seals. Fluid lost through the shaft opening 76 is replaced by fluid through the check valve 173 and, in the example given, amounts to two or more gallons per minute.

The water cooling jacket for the motor 'shell 16 is attached to a suitable source of Water or other cooling fluid (not shown) by means of the inlet 227, and the water flows around the coils 225 through the outlet 226. Also, the coils are open at each end in the Water jacket and will pick up water for flow through the coils from that present in the Water jacket, thus giving a spiral effect to the water flow and furnishing a double path, very eflicient arrangement which will remove a major portion of the heat from the motor area and retain the motor 12 at not to exceed its maximum operating temperature.

There has thus been described a combination cooling system involving the thermal plate cooling system, the zigzag water cooling system in the pump cover 17, the motor and seal cooling and lubricating system, and the water jacket system for cooling the motor shell 16. These systems are interrelated and coordinated to maintain the temperature of the motor 12 at its proper level, to lubri cate and cool the seals, and, at the same time, "deter the:

flow of heat from the main pump 11 to the motor while not seriously reducing the heat in the main pumpchamber.

It may be noted that the pump and motor assembly herein is provided with a very efficient and advantageous meansfor servicing and assembly. The motor shell 16, motor shaft 66, pump cover body 17, thermal plate 39 and its integral pump difluser 46, and impeller '77 may be removed from the pump case 15 by removal'of the' nuts 23. The impeller may be removedby removal of the cap screw' 79 and threaded collar 78. When this has been done, the thermal plate 39 is removed by removing'the nuts 45; and removal of the thermal plate automatically removes its integral pump diffuser 46, allowing full access for service thereto. A replacement thermal plate-the thermal plate and integral pump diffuser are subject to considerable wear and sometimes need replacement-may 1 7 be placed in position and the parts reassembled in the reverse order from that described for disassembly.

After the thermal plate has been removed, the seal area may be removed for repair and replacement by removing the cap screws 50. Thus, it is easy to obtain access to the seal area without removing the pump cover body 17. However, should access be needed to the motor, the pump cover body 17 can be lifted from the assembly when the nuts 23, which hold the pump case 15 assembled to the flange 22 on the motor shell 16, have been removed. Thus, ready access can be had to either the motor or the seal area.

The auxiliary pump assembly 13 is equally accessible to entry for repair and replacement by removal of the motor shell cover 18 and bearing housing cover 34.

It is believed that a very compact, efficient and easily serviceable arrangement, which is novel and an improvement over prior structures, has been provided.

While the specific details of the invention have been herein shown and described, changes and alterations may be made without departing from the spirit of the invention.

I claim:

1. A compact, unitary, pump and motor assembly for pumping high pressure-high temperature fluids, such as for processing hydrocarbons in a reactor circulating system, comprising in combination in a housing assembly:

(a) container means comprising a pump case containing a fluid at high temperature and under high pressure to be pumped and having therein a pump impeller;

(b) a motor shell removably attached to said pump case and containing an electric motor having a stator and a rotor;

(c) a pump cover body between said pump case and said electric motor;

(d) a combined thermal plate and pump diffuser between said pump cover body and said impeller, said thermal plate forming a closure for said pump case and said diffuser extending into said pump case and surrounding said impeller, said thermal plate additionally engaging the surface of said pump cover body;

(e) auxiliary pump means in said motor shell;

(f) a drive shaft driven by said rotor and extending through said pump cover body and said thermal plate into said pump case and being drivingly connected to said impeller and to said auxiliary pump; and

(g) shaft seal means comprising a mechanical seal assembly surrounding said drive shaft and sealing against flow of fluid from the pump case into the motor shell;

wherein:

(h) the combined thermal plate and pump diffuser has a shaft opening;

(i) the pump cover body has a bore aligned with such shaft opening and which pump cover body is con tiguous to said thermal plate when the latter is in position in said pump and motor assembly;

(i) said thermal plate has concentric groove means on its surface contiguous to said pump cover body and forming with said pump cover body a spiral-like fluid passage;

(k) a fluid inlet to said passage adapted to be connected to a source of fluid under pressure; and

(I) said fluid passage having a discharge opening whereby fluid entering said inlet flows through said passage and is discharged into said pump case through said pump cover body bore and said shaft opening.

2. A compact, unitary, pump and motor assembly for pumping high pressure-high temperature fluids, such as for processing hydrocarbons in a reactor circulating system, comprising in combination in a housing assembly:

(a) container means comprising a pump case containing a fluid at high temperature and under high pressure to be pumped and having therein a pump impeller;

(b) a motor shell removably attached to said pump case and containing an electric motor having a stator and a rotor;

(c) a pump cover body between said pump case and said electric motor;

(d) a combined thermal plate and pump diffuser between said pump cover body and said impeller, said thermal plate forming a closure for said pump case and said diffuser extending into said pump case and surrounding said impeller, said thermal plate additionally engaging the surface of said pump cover body;

(e) auxiliary pump means in said motor shell;

(f) a drive shaft driven by said rotor and extending through said pump cover body and said thermal plate into said pump case and being drivingly connected to said impeller and to said auxiliary pump; and

(g) shaft seal means comprising a mechanical seal assembly surrounding said drive shaft and sealing against flow of fluid from the pump case into the motor shell;

wherein:

(h) the combined thermal plate and pump diffuser is removably attached to the pump cover body and has a shaft opening in the center thereof;

(i) the pump cover body has a bore in the center thereof aligned with the shaft opening in the thermal plate and also has astainless steel layer contiguous to the thermal plate when the latter is attached to the pump cover body;

(j) the thermal plate has a series of interconnecting generally concentric grooves on its surface contiguous to the pump cover body, and forming with the pump cover body a spiral-like fluid passage, a fluid inlet to said passage adapted to be connected to a source of fluid, said fluid passage opening into said bore whereby fluid entering said inlet flows through said passage and is discharge into said bore.

3. A compact, unitary, pump and motor assembly for pumping high pressure-high temperature fluids, such as for processing hydrocarbons in a reactor circulating system, comprising in combination in a housing assembly:

(a) container means comprising a pump case contain ing a fluid at high temperature and under high pressure to be pumped and having therein a pump impeller; I

(b) a motor shell removably attached to said pump case and containing an electric motor having a stator and a rotor;

(c) a pump cover body between said pump case and said electric motor;

(d) a combined thermal plate and pump diffuser between said pump cover body and said impeller, said thermal plate forming a closure for said pump case and said diffuser extending into said pump case and surrounding said impeller, said thermal plate additjionally engaging the surface of said pump cover (e) auxiliary pump means in said motor shell;

(f) a drive shaft driven by said rotor and extending through said pump cover body and said thermal plate into said pump case and being drivingly connected to said impeller and to said auxiliary pump; and

(g) shaft seal means comprising a mechanical seal assembly surrounding said drive shaft and sealing against flow of fluid from the pump case into the motor shell;

wherein: a

(b) said pump cover body has a series of inwardly extending bores connected together to form a con- 19 tinuous zigzag-like fluid passage through said pump cover body;

(i) an inlet connection to said fluid passage adapted to be connected to a source of cooling fluid, such as Water; and

(j) an outlet connection for said passage whereby fluid completing its circuit through said inlet and said bores is discharged from said outlet after performing its cooling function.

4. A compact, unitary, pump and motor assembly for pumping high pressure-high temperature fluids, such as for processing hydrocarbons in a reactor circulating system, comprising in combination in a housing assembly:

(a) container means comprising a pump case contain ing a fluid at high temperature and under high pressure to be pumped and having therein a pump impeller;

(b) a motor shell removably attached to said pump case and containing an electric motor having a stator and a rotor;

(c) a pump cover body between said pump case and said electric motor;

(d) a combined thermal plate and pump diffuser between said pump cover body and said impeller, said thermal plate forming a closure for said pump case and said diffuser extending into said pump case and surrounding said impeller, said thermal plate additionally engaging the surface of said pump cover body;

(e) auxiliary pump means in said motor shell;

(f) a drive shaft driven by said rotor and extending through said pump cover body and said thermal plate into said pump case and being drivingly connected to said impeller and to said auxiliary pump; and

(g) shaft seal means comprising a mechanical seal assembly surrounding said drive shaft and sealing against flow of fluid from the pump case into the motor shell;

wherein:

(h) said electric motor stator is within and contiguous with said motor shell and has a series of axial fluid passages across said stator between the stator and said shell;

(i) means comprising a stator spacer sleeve at one end of said stator and a second stator spacer sleeve at the other end of said stator having fluid conduit means on the outer circumference of each spacer sleeve and in register with the axial passages across the stator, each of said spacer sleeves having a plurality of said fluid conduit means, each of which is in fluid contact with a portion only of said stator passages; and

(j) an inlet for fluid under pressure in one said stator spacer sleeve and a discharge outlet for said fluid in the other said stator spacer sleeve, the arrangement being such that a sinuous fluid flow path through said spacer sleeves and across said stator is provided whereby the fluid is caused to cross said stator in an axial direction a plurality of times in traversing the entire circumference of said stator.

5. A compact, unitary, pump and motor assembly for pumping high pressure-high temperature fluids, such as for processing hydrocarbons in a reactor circulating system, comprising in combination in a housing assembly:

(a) container means comprising a pump case containing a fluid at high temperature and under high pressure to be pumped and having therein a pump impeller;

(b) a motor shell removably attached to said pump case and containing an electric motor having a stator and a rotor;

(c) a pump cover body between said pump case and said electric motor;

(d) a combined thermal plate and pump diffuser between said pump cover body and said impeller, said thermal plate forming a closure for said pump case and said diffuser extending into said pump case and surrounding said impeller, said thermal plate additionally engaging the surface of said pump cover body;

(e) auxiliary pump means in said motor shell;

(f) a drive shaft driven by said rotor and extending through said pump cover body and said thermal plate into said pump case and being drivingly connected to said impeller and to said auxiliary pump; and

(g) shaft seal means comprising :a mechanical seal assembly surrounding said drive shaft and sealing against flow of fluid from the pump case into the motor shell;

wherein:

(h) said electric motor is provided with a series of axial fluid passages across its stator formed by alternating stator ridges and stator grooves, such stator ridges being positioned in and contiguous to the motor housing assembly whereby the latter forms one surface of each of said passages;

(i) an upper stator spacer sleeve and a lower spacer sleeve located respectively above and below said stator and contiguous thereto, said spacer sleeves having fluid inlet and exit means and raised lands and a series of spaced, staggered ridges, forming with said motor shell conduit spaces in fluid communication with the passages formed across the stator, whereby fluid entering the lower spacer sleeve flows across a series of the fluid passages formed on the stator into a conduit space on the upper spacer sleeve, is directed back across another series of passages formed on the stator into a bottom conduit space on the bottom spacer sleeve, is directed back through another series of passages formed on the stator into a second top conduit space of the upper spacer sleeve, is directed :back across still another series of stator passages into a second bottom conduit space on the bottom spacer sleeve, is directed across the stator through still another series of stator passages into a discharge space in the upper spacer sleeve, thereby crossing the said stator in axial directions a plurality of times in :a sinuous flow pattern in flowing once around the circumference of said stator, said lower spacer sleeve having connections to a source of fluid and said upper spacer sleeve discharge means for said fluid.

6. A pump and motor assembly as set forth in claim 4 wherein:

(a) said auxiliary pump means has a fluid inlet in fluid communication with a source of fluid under pressure for lubricating and cooling parts of said pump and motor assembly, and has a fluid outlet connection to said inlet in one said spacer sleeve;

(b) said pump cover body has a bore therethrough through which said drive shaft extends and a mechanical seal assembly surrounding said drive shaft and located in said pump cover body bore;

(0) said thermal plate having a shaft opening therethrough for said drive shaft, said shaft opening being in alignment with said bore of said pump cover body;

(d) fluid chamber means comprising an annular fluid chamber into which fluid is discharged from said spacer sleeve discharge outlet after it has passed over the entire circumference of said stator;

(e) fluid passage means comprising at least one fluid passage extending from said fluid chamber means to said pump cover body bore;

(f) an axially extending bore in said drive shaft, fluid passage means comprising a hole in said drive shaft in communication with said bore in said pump cover body, whereby a portion of the fluid entering said last-mentioned bore from the fluid chamber means through the fluid passage above-mentioned is conducted to the bore in said drive shaft;

(g) means comprising a pressure and flow reducing cell in said pump cover bore and in communication with fluid from said fluid chamber diverting a re- (b) a thermal plate in the bottom of said pump case,

said plate having an opening;

(c) a pump cover body adjacent to said thermal plate and having a bore therethrough aligned with the opening of said thermal plate, said pump cover body duced portion of said fluid through said thermal plate having a mechanical seal assembly located in said drive shaft opening; bore;

(h) means comprising at least one passage from said (d) an auxiliary pump in said motor shell;

drive shaft bore discharging fluid therefrom into said (e) a drive shaft attached to said rotor whereby it is motor shell; and 1Q driven by said electric motor, said drive shaft also (i) passage means through said motor between said being attached in driving relation to said auxiliary stator and said rotor and into said auxiliary pump pump and said impeller and extending from said inlet, the arrangement being such that fluid pumped motor shell through said pump cover body bore, said by said auxiliary pump is carried across the stator mechanical seal assembly, and said thermal plate in contact with the motor shell, through said passages opening into said pump case; in the pump cover body, over said mechanical seal (f) fluid temperature regulating and lubricating means assembly and a portion thereof going through said for said pump and motor assembly comprising a thermal plate opening, and the remainder thereof thermal plate cooling system, a pump cover body going through said drive shaft back into said. motor zigzag water circulatin system, a motor cooling and shell, through said motor and into the inlet for said seal lubricating system using fluid pressure from said auxiliary pump where it is again recirculated. auxiliary pump, which motor cooling and seal lub- 7. A pump and motor assembly as set forth in claim ricating system includes a sinuous stator cooling fluid 6 wherein: flow path With fluid connections in said pump cover (a) said motor shell has cooling means comprising to said mechanical seal assembly and return fluid a heat exchange shell surrounding said motor shell connections through said drive shaft and said motor and attached thereto in fluid-tight relation;, to said auxiliary pump means;

(b) inlet connections for a cooling fluid in said heat (g) a water jacket cooling means comprising a heat exchange shell and a discharge port from said heat exchange shell with an open ended spiral tube thereexchange shell; and in located about the outer circumference of said (c) a spiral tube having unconnected inlet and outlet motor shell; and

openings entirely within said shell whereby a por- (h) fluid connections for a source of fluid to said tion of the fluid entering said heat exchange shell thermal plate cooling system, said pump cover body flows around said spiral tube to said discharge port, Water Circulating System, Said auxiliary P mp and and the remainder of said fluid flows through said Said P excjhange f y the temperature Spiral tube and back into said heat exchange shell of said electric motor is maintained within tolerable prior to discharge from said discharge port. 11mm 8. A compact, unitary, pump and motor assembly for References Clted pumping high pressure-high temperature fluids compris- UNITED STATES PATENTS ing, in combination: 2,887,062 5/1959 Cametti et al.

(a) a housing assembly comprising a pump case having 2,936,774 5 /19 Holley et 1 therein a pump impeller and containing fluid at 3,215,083 11/1965 Sarles et a1. high temperature and under high presssure to be pumped, a motor shell removably attached to said 4 ROBERT WALKER, Primary mincr pump case and containing an electric motor having a stator and a rotor, said motor shell having a motor shell cover;

US. Cl. X.R.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3 7 9 Dated November 18, 1969 Inventor(s) Rowland E. 138.11

It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 8, line 65, "35" should be --l35--; line T t, after "from" should be --the motor lubrication system, and the mixture iS diS- Column 9, line 1, omit "the motor is dis-"5 line 3, "16" should be --l15--.

Column 11, line 13, "b state" should be --be stated--; line 59, after "top" should be --end--.

Column 12, line #5, "recycle" should be --recycled--.

Column 13, line 2, "receive" should be --receives--.

Column 15, line 72, "axilially" should be --axially--.

all $20 an SEALED M20191;

SEAL) Atteat:

Edward mm 1:. m. Atleaung Offioor flomissioner of Patents ORM PC4050 0- lmrnMu-nr nnqvn-cma 

